CN101454595A - Two-planetary electrically variable transmissions with multiple fixed ratios - Google Patents

Two-planetary electrically variable transmissions with multiple fixed ratios Download PDF

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Publication number
CN101454595A
CN101454595A CNA2007800192141A CN200780019214A CN101454595A CN 101454595 A CN101454595 A CN 101454595A CN A2007800192141 A CNA2007800192141 A CN A2007800192141A CN 200780019214 A CN200780019214 A CN 200780019214A CN 101454595 A CN101454595 A CN 101454595A
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China
Prior art keywords
motor
parts
torque transmitter
generator
variable transmission
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Granted
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CNA2007800192141A
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Chinese (zh)
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CN101454595B (en
Inventor
N·巴克诺尔
T·辛格
J·A·迪默
A·G·霍尔姆斯
J·D·亨里克森
J·E·莱尔曼
M·拉哈文
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GM Global Technology Operations LLC
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GM Global Technology Operations LLC
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Publication of CN101454595A publication Critical patent/CN101454595A/en
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Publication of CN101454595B publication Critical patent/CN101454595B/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/727—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path
    • F16H3/728—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path with means to change ratio in the mechanical gearing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/40—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the assembly or relative disposition of components
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/44—Series-parallel type
    • B60K6/445—Differential gearing distribution type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B60K6/54—Transmission for changing ratio
    • B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K1/02—Arrangement or mounting of electrical propulsion units comprising more than one electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/0866—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/0866—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft
    • F16H2037/0873—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft with switching, e.g. to change ranges
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
    • F16H2037/104—Power split variators with one end of the CVT connected or connectable to two or more differentials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
    • F16H2037/105—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts characterised by number of modes or ranges, e.g. for compound gearing
    • F16H2037/106—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts characterised by number of modes or ranges, e.g. for compound gearing with switching means to provide two variator modes or ranges
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2064—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using at least one positive clutch, e.g. dog clutch
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • General Engineering & Computer Science (AREA)
  • Electric Propulsion And Braking For Vehicles (AREA)
  • Structure Of Transmissions (AREA)
  • Hybrid Electric Vehicles (AREA)
  • Arrangement Of Transmissions (AREA)

Abstract

The electrically variable transmission family of the present invention provides low-content, low-cost electrically variable transmission mechanisms including first and second differential gear sets, a battery, two electric machines serving interchangeably as motors or generators, up to six selectable torque-transfer devices and possibly a dog clutch. The selectable torque transmitting devices are engaged to yield an EVT with a continuously variable range of speeds (including reverse) and at least four mechanically fixed forward speed ratios. The torque transmitting devices and the first and second motor/generators are operable to provide five operating modes in the electrically variable transmission, including battery reverse mode, EVT reverse mode, reverse and forward launch modes, continuously variable transmission range mode, and fixed ratio mode.

Description

Duplicate rows planetary electrically variable formula speed changer with a plurality of fixed ratios
Technical field
[0001] the present invention relates to electrically variable transmission (electrically variabletransmission), it has the variable velocity that adopts power dividing operates than the selectivity of scope (range) and employing fixed speed ratio, and has two planetary gear set, two motor (motor)/generator (generator) and reach six torque transmitter.
Background technique
[0002] present, internal-combustion engine, especially reciprocating piston type internal-combustion engine advances most vehicle.This class motor is to be used for efficient relatively, small-sized, lightweight and the cheap mechanism that highly enriched transformation of energy with the fuel form becomes effective mechanical output.The new work transmission system that can be used for internal-combustion engine and can reduce fuel consumption and pollutant emission has very big benefit to the public.
[0003] very big change can take place to the demand that internal-combustion engine proposed in vehicle usually, and this makes the consumption of fuel and the ideal situation that discharging has exceeded this class motor.Usually, vehicle is to be advanced by motor, and this kind motor starts from cold state with relative less battery by miniature motor, is placed apace then under the load of self-propelling instrument and accessory.This kind motor is also being operated under the very large-scale speed and under very large-scale load, and is on average operating under its 1/5 peak output output approximately usually.
[0004] transmission for vehicles is passed to the remaining part of drive system with mechanical output from motor usually, for example, and fixing main reducing gear gearing, axle and wheel.Typical mechanical transmission allows power operation to have level of freedom, and this normally realizes by the following: the alternate selection of five or six different driving ratios; The selection of neutral gear, it allows motor to operate annex under the situation of stationary vehicle; And clutch or torque converter, it is used for carrying out transition stably and starts vehicle from stationary state when engine rotation between each drive ratio.The selection of Transmission gear allow usually power with multiple torque than and reduction speed ratio, with moment of torsion reduce than with speed multiplication than (it is called hypervelocity and compares) or reverse gear than the remaining part that is passed to drive system.
[0005] generator can be transformed into electric power with the mechanical output from motor, and motor can be transformed into the mechanical output that is used for the driver for vehicle remaining part with electric power again with different moments of torsion and speed with returning.This layout allows torque ratio and the velocity ratio between motor and the drive system remaining part to carry out continuous variation in the limit of motor (electric machinery).Battery as the propeller power source can be added into this layout, mix electrical drive system thereby form tandem (series).
[0006] this serial hybrid allows to operate under there are the situation of certain independence in motor and propelled vehicles required moment of torsion, speed and power, so the may command motor improves and discharges and efficient.This system allows motor to be attached to the motor that motor is used as piloting engine.This system also allows motor to be attached to drive the remaining part of system to be used as generator, thereby brakes the energy recovery that will produce owing to vehicle slows in battery by electric power storage (regenerative).The tandem electric driver is subjected to following puzzlement at 2: be enough in generator all engine powers are transformed into electric energy and electric energy are transformed into the weight and the cost of the motor of mechanical energy drive motor from mechanical energy; The useful power that is lost in these transfer processes.
[0007] the power dividing speed changer can use and be generally understood as " differential gearing " but continually varying moment of torsion and velocity ratio between realizing input and exporting.Electrically variable transmission can use differential gearing to carry the part of its transmission power by pair of motors/generator.But the remaining part of variator power flows through the full machinery of another fixed ratio or ratio alternate selection, direct parallel route.
[0008] know as those skilled in the art, a kind of differential gearing can be a planetary gear set.The preferred embodiment that planetary gear system is normally used in the differential gear invention, it has small-sized and can realize the advantage of different moments of torsion and velocity ratio in all parts of planetary gear set.Yet, be always by rotating speed in the average weighted layout of two other element speeds and use angular wheel or other gear at least one element of gear train, just can not need to construct the present invention under the planetary situation.
[0009] the hybrid electric vehicle speed variator system also comprises one or more apparatus for storing electrical energy.Typical devices is a chemical storage batteries, but also can comprise capacitive device or mechanical device on (for example, electric driving flywheel).The mechanical output power of apparatus for storing electrical energy permission from the speed variator system to the vehicle is different from the mechanical input power from the motor to the speed variator system.This battery or other device also allow motor to utilize speed variator system to start and allow the accumulation of energy car brakeing.
[0010] electrically variable transmission in the vehicle can be delivered to main reducing gear output with mechanical output from the motor input simply.For this reason, the electric power that motor/generator produced can lose the electric power that is consumed with another motor/generator by balancing electric power.By using above-mentioned storage battery, the electric power that motor/generator produced can be greater than or less than the electric power that another motor/generator consumes.Sometimes, can allow two motor/generators all to be used as motor, be particularly useful for helping motor to carry out vehicle and quicken from the electric power of this battery.Sometimes, two motor all can be used as generator with to battery charge, especially in the accumulation of energy car brakeing.
[0011] the successful replacer of tandem hybrid transmission is the electrically variable transmission of two scopes, input shunting and compound shunting, it is produced at present and is used for the traffic bus, as announce on August 3rd, the 1999 and U.S. Patent No. 5 common transfer of the application's case of authorizing Michael Roland Schmidt, 931,757, in disclosed, and the mode that this patent is quoted in full is incorporated herein.This kind speed changer utilizes input device to accept from the power of vehicle motor and utilizes power output device to come transmitted power with powered vehicle.First motor/generator and second motor/generator (for example are connected to energy storage device, battery), so as energy storage device can accept from the power of first motor/generator and second motor/generator and power can be supplied to first motor/generator and second motor/generator.Control unit is being regulated power circuit among energy storage device and the motor/generator and between first motor/generator and second motor/generator.
[0012] can optionally realize operating than operator scheme than the operator scheme or second variable velocity by the clutch that use has first torque transmitter and the second torque transmitter character with first variable velocity.In first pattern, form input-power-shunting velocity ratio scope by applying first clutch, and the speed of the output speed of speed changer and a motor/generator is proportional.In second pattern, form compound-power-shunting velocity ratio scope by applying second clutch, and the speed of the output speed of speed changer and arbitrary motor/generator is all disproportionate, but the algebraically linear combination of these two motor/generator speed.Can optionally realize the fixedly operation of gear ratio by applying two clutches.The operation of this speed changer under neutral mode can optionally realize by discharging two clutches, thereby make motor and two motor/generators and speed changer output disengaging.This speed changer comprises at least one mechanical. points and comprise at least two mechanical. points under its second operator scheme under its first operator scheme.
[0013] U.S. Patent No. 6,527,658 disclose a kind of two planetary gear set, two motor/generators and two clutches of utilizing provides the electrically variable transmission of importing triage operator pattern, compound triage operator pattern, neutral gear operator scheme and reverse gear operator scheme, this U. S. Patent is authorized people such as Holmes, announce on March 4th, 2003, be incorporated herein with the common mode of transferring the possession of and quoting in full of the application's case.Two planetary gear set all can be simple planetary gear set, perhaps one can be compound individually.Electric-controlled parts is regulated the power circuit among energy storage device and two motor/generators.This speed changer provides two scopes or the pattern of electrically variable transmission (EVT) operation, thereby optionally provides input-power-shunting speed than scope and compound-power-shunting velocity ratio scope.Also optionally realize a fixed speed ratios.
Summary of the invention
[0014] the invention provides an electrically variable transmission series, it provides several advantages that surpass the conventional automatic transmission use in hybrid vehicle, these advantages comprise improved vehicle accelerating ability energy, via energy storing brake and only electronic mode idle running and start and the fuel economy that is improved and the market characteristics of attraction.The objective of the invention is provides best as far as possible energy efficiency and discharging for given motor.In addition, also seek optimal performance, capacity, package dimension and the ratio coverage area of speed changer.
[0015] electrically variable transmission series of the present invention provides low volume, electrically variable transmission mechanism cheaply, and it comprises that first and second differential gear set, battery, two are interchangeably as the motor of motor or generator and six selectable torque transmitter nearly.Additionally, can provide dog-clutch.Preferably, this differential gear set is a planetary gear set, for example simple set of gears or composite teeth wheels (it comprises the Ravigneaux gear train), but also can implement other arrangement of gears angular wheel or the differential gearing of off-axis (for example, with respect to).
[0016] in this manual, first planetary gear set or second planetary gear set can (that is, from left to right, count first to second from right to left) with any order.
[0017] each in these two planetary gear set all has three parts.First parts of each planetary gear set, second parts or the 3rd parts can be any in sun gear, ring gear or the carriage member, perhaps are chosen as small gear.
[0018] each carriage member can be single small gear carriage member (simply) or double pinion carriage member (compound).
[0019] input shaft is connected constantly or optionally with at least one parts of planetary gear set.Output shaft is connected constantly with at least one parts in the planetary gear set.
[0020] optional first interconnecting member makes first parts of first planetary gear set be connected constantly with first parts of second planetary gear set.
[0021] first torque transmitter makes the parts of first planetary gear set optionally be connected with the parts of the input block or second planetary gear set.
[0022] second torque transmitter makes the parts of second planetary gear set optionally be connected with the parts of first planetary gear set, this to parts be different from connected by first torque transmitter that to parts.
[0023] the 3rd torque transmitter makes the parts of first planetary gear set optionally be connected with the parts or the input block of second planetary gear set.
[0024] the 4th torque transmitter makes the parts of first planetary gear set optionally be connected with fixed component (gearbox case/housing).
[0025] the 5th torque transmitter makes the parts of second planetary gear set optionally be connected with fixed component (gearbox case/housing)
[0026] in Ren Xuan the 6th torque transmitter and the motor/generator is parallel is connected to prevent that optionally this motor/generator from rotating.
[0027] torque transmitter as break can suitably be embodied as traditional frictin braek, dog-clutch, overrunning clutch or selectable one-way clutch.Rotary clutch can suitably be embodied as traditional friction clutcch, dog-clutch, overrunning clutch or selectable one-way clutch.
[0028] first motor/generator is mounted to the parts that case of transmission also is connected to the parts of first planetary gear set constantly or optionally is connected to first planetary gear set or second planetary gear set via dog-clutch.First motor/generator also can comprise inclined to one side gearing (offset gearing).Dog-clutch (if present) allows first motor/generator to switch between the cheek of first planetary gear set or second planetary gear set.Dog-clutch can reduce the clutch spin loss, and allows motor/generator to operate in the operating range of whole speed changer.This dog-clutch can be substituted by a pair of traditional torque transmitter.
[0029] second motor/generator is mounted to case of transmission and is connected to first planetary gear set constantly or the parts of second planetary gear set.This second motor/generator connects can comprise inclined to one side gearing.
[0030] optionally torque transmitter becomes to engage in combination, but has the EVT of the forward velocity ratio of continually varying velocity range (it comprises reverse gear) and at least four mechanical fixation with generation." fixed speed ratio " is that the mechanical output that inputs to speed changer mechanically is passed to the operational circumstances that does not have any power circuit (that is, almost nil) in output and the motor/generator.The operation that electrically variable transmission can be approximate full engine power optionally realizes several fixed speed ratios, and can be more small-sized and lighter under given maximum capacity.When operating under the situation that can not use motor/generator at engine speed near the optimum state, fixed ratio operation can make that also fuel consumption is lower.This fixed ratio operation is when because lower battery-operated and can not obtain to be used to satisfy the demand of reverse gear grade ability when electric moment of torsion is auxiliary, and is used for the cold weather operation.By compatibly selecting the gear ratio of planetary gear set, can realize various fixed speeds ratios and variable ratio scope (ratio spread).
[0031] electrically variable transmission of the present invention has compound shunting and input branch stream architecture.Compound shunting refers to the framework that the speed changer input and output are not connected directly to motor/generator.This allows to reduce motor/generator desired size and cost when realizing desired vehicle performance.In input shunting design, one in the motor/generator directly is connected to output.
[0032] design of Ti Chuing all designs for double-mode or triplex mode design (or double scope or triple scope), wherein, in forward gears EVT operation period, a torque transmitter is disengaged, and another torque transmitter engages, thus change pattern or scope.Multiplex mode design makes switching (the compound output steering etc. that branches to) the match operation needs better between the different operation modes, and reduces the energy of electric elements load/speed and use simultaneously.These torque transmitters and first motor/generator and second motor/generator can be operated, so that five kinds of operator schemes to be provided in electrically variable transmission, but it comprises battery reverse gear mode, EVT reverse gear mode, reverse gear and forward gears originate mode continually varying slewing range pattern and fixed ratio pattern.
[0033] suitably, break can be embodied as the conventional break based on friction, tooth clutch, overrunning clutch, selectable one-way clutch etc.Suitably, the clutch of rotation can be embodied as the conventional clutch based on friction, tooth clutch, overrunning clutch, selectable one-way clutch etc.
[0034] consult followingly about implementing the detailed description of best mode of the present invention in conjunction with the accompanying drawings, above-mentioned feature and advantage of the present invention and other feature and advantage are just apparent.
Description of drawings
[0035] Fig. 1 a is the schematic representation of dynamical system, and it comprises the electrically variable transmission with the present invention's series parts;
[0036] Fig. 1 b is operator scheme table and the fixed ratio pattern list that illustrates some operating characteristics of dynamical system shown in Fig. 1 a;
[0037] Fig. 2 a is the schematic representation of dynamical system, and it has the electrically variable transmission that comprises another serial parts of the present invention;
[0038] Fig. 2 b is operator scheme table and the fixed ratio pattern list that illustrates some operating characteristics of dynamical system shown in Fig. 2 a;
[0039] Fig. 3 a is the schematic representation of dynamical system, and it has the electrically variable transmission that comprises another serial parts of the present invention;
[0040] Fig. 3 b is operator scheme table and the fixed ratio pattern list that illustrates some operating characteristics of dynamical system shown in Fig. 3 a;
[0041] Fig. 4 a is the schematic representation of dynamical system, and it has the electrically variable transmission that comprises another serial parts of the present invention; With
[0042] Fig. 4 b is operator scheme table and the fixed ratio pattern list that illustrates some operating characteristics of dynamical system shown in Fig. 4 a;
Embodiment
[0043] with reference to Fig. 1 a, shown dynamical system 10, it comprises the motor 12 of a preferred embodiment that is connected to modified model electrically variable transmission (EVT) (it is totally by numeral 14 expressions).Speed changer 14 is designed for receiving its at least a portion from the driving power of motor 12.As shown in the figure, motor 12 has the output shaft as the input block 17 of speed changer 14.Transient torque damper (not shown) also may be implemented between the input block 17 of motor 12 and speed changer 14.
[0044] in this illustrated embodiment, motor 12 can be the mineral fuel motor, for example, is suitable for providing its diesel engine that available power of transmitting with constant per minute rotating speed (RPM) is exported easily.
[0045] no matter which kind of means motor 12 adopts be connected to speed changer input block 17, and speed changer input block 17 all may be operably coupled to the planetary gear set in the speed changer 14.The output block 19 of speed changer 14 is connected to main reducing gear 16.
[0046] speed changer 14 has utilized two differential gear set of the character that preferably has planetary gear set 20 and 30.Planetary gear set 20 is used the outer gear part 24 that is commonly referred to ring gear.Ring gear component 24 is external in the internal gear part 22 that is commonly referred to sun gear.Carriage member 26 rotatably supports a plurality of planetary pinions 27, so that each planetary pinion 27 engages the outer ring geared parts 24 and the interior sun gear parts 22 of first planetary gear set 20 in the mode of engagement.
[0047] planetary gear set 30 also has the outer gear part 34 that is also referred to as ring gear usually, and outer gear part 34 is external in the internal gear part 32 that is commonly referred to the sun gear parts equally.A plurality of planetary gear set 37 also rotatably are installed in the carriage member 36, so that each planetary gear member 37 engages the outer ring geared parts 34 and the interior sun gear parts 32 of planetary gear set 30 simultaneously in the mode of engagement.
[0048] first interconnecting member 70 makes the ring gear component 24 of planetary gear set 20 be connected constantly with the sun gear parts 32 of planetary gear set 30.
[0049] first preferred embodiment 10 also comprises first motor/generator 80 and second motor/generator 82.The stator of first motor/generator 80 is fixed to gearbox case 60.The rotor of first motor/generator 80 is fixed to the sun gear parts 22 of planetary gear set 20.
The stator of [0050] second motor/generator 82 also is fixed to gearbox case 60.The rotor of second motor/generator 82 is fixed to the sun gear parts 32 of planetary gear set 30.
[0051] first torque transmitter (for example, input clutch 50) makes the carriage member 26 of planetary gear set 20 optionally be connected with input block 17.Second torque transmitter (for example, clutch 52) makes the sun gear parts 22 of planetary gear set 20 optionally be connected with the ring gear component 34 of planetary gear set 30.The 3rd torque transmitter (for example, input clutch 54) makes sun gear parts 22 optionally be connected with input block 17.The 4th torque transmitter (for example, break 55) makes ring gear component 34 optionally be connected with gearbox case 60.The 5th torque transmitter (for example, break 57) makes carriage member 26 optionally be connected with gearbox case 60.The 6th torque transmitter (for example, break 58) and 82 parallel connections of motor/generator optionally to brake its rotation.First torque transmitter 50, second torque transmitter 52, the 3rd torque transmitter 54, the 4th torque transmitter 55, the 5th torque transmitter 57 and the 6th torque transmitter 58 are used to help to select the operator scheme of hybrid type speed changer 14, and this will intactly explain hereinafter.
[0052] the output driver part 19 of speed changer 14 is fixed to the carriage member 36 of planetary gear set 30.
[0053] turn back to elaboration about power source now, according to above stated specification and with reference to Fig. 1 a, be apparent that, speed changer 14 is from motor 12 received power optionally.The hybrid type speed changer is electric power source 86 received powers from may be operably coupled to controller 88 also.Electric power source 86 can be one or more batteries.Can use can provide or store and other electric power source (for example, fuel cell) of the electric power of providing and delivering substitutes battery, and this can't change principle of the present invention.
Common operation Consideration
[0054] one of major control device is the driving scope selector (not shown) of knowing, and its commander's electronic control unit (ECU88) is configured speed changer so that realize parking, reverse gear, neutral gear or forward drive scope.The second major control device and the 3rd major control device are accelerator pedal (not shown) and brake pedal (also not showing).ECU is called as " operator's demand " from the information that these three major control sources obtain.ECU is also from the information of a plurality of sensors (input and output) acquisition about following state: torque transmitter (it is applied in or is released), engine output torque, (a plurality of) standard cell or its capacity level and selected vehicle component temperature.ECU determines needed information, suitably regulates the demand of selectivity control member speed changer or that be associated with speed changer with the operation response person then.
[0055] the present invention can use simple planetary group or dual planetary gear group.In the simple planetary group, list group planetary pinion supporting usually is so that rotate on rotatable carriage member own.
[0056] in the simple planetary group, when sun gear is maintained fixed and power when being applied to the ring gear of simple planetary group, therefore planetary pinion will rotate in response to the power that is applied to ring gear and around fixing sun gear " walking " circumferentially, thereby the realization carriage member rotates along the direction identical with the ring gear sense of rotation.
[0057] when any two parts of simple planetary group rotated along same direction and with same speed, the 3rd parts can be forced to same speed and along same direction and rotate.For example, when sun gear and ring gear during along same direction and with same speed rotation, planetary pinion is around himself axis rotation, but as chock whole unit locked together, thereby realizes so-called direct driving.That is to say that carriage member and sun gear and ring gear together rotate.
[0058] yet, when two geared parts rotate along same direction but with friction speed, the sense of rotation of the 3rd geared parts can be determined by visual analysis usually simply, but described in many cases direction and not obvious and only know that the number of teeth that exists on all geared parts of planetary gear set could determine exactly.
[0059] as long as carriage member is prevented from rotating freely and power is applied to sun gear or ring gear, then planetary gear member all can be as free pulley.Like this, driven member is with the direction rotation opposite with driving part.Therefore, in a lot of gearbox arrangement, when selecting reverse drive range, engaged as the torque transmitter of break can frictionally activate carriage member and thereby stop its rotation so that the power that is applied to sun gear swivel becket generating gear in opposite direction.Therefore, if ring gear may be operably coupled to the driving wheel of vehicle,, and thereby make the direction of vehicle self reverse just then this kind layout can make the sense of rotation of wheel reverse.
[0060] in one group of simple planetary pinion, if any two rotating speed in known sun gear, planet carrier parts and the ring gear, just then the speed of the 3rd parts could use simple rule to determine.The speed after the number of teeth weighting is proportional separately through it with sun gear and ring gear all the time for the rotating speed of carriage member.For example, in same gear train, ring gear can have the number of teeth that doubles sun gear.The speed of carriage member be 2/3 ring gear speed and 1/3 speed sun gear and.If a rotation in the opposite direction in these three parts, then the arithmetic sign of this parts speed is born in mathematical computations.
[0061] if do not consider the quality of these gears, the acceleration or the friction in the gear train (all these influences are all less relatively in the good speed changer of design) of these gears, then the moment of torsion on sun gear, carriage member and the ring gear can be relevant simply each other.The moment of torsion that is applied to simple planetary group sun gear must balance be applied to the moment of torsion of ring gear, and the number of teeth in these moments of torsion and these gears on each is proportional.For example, its number of teeth in gear train is doubled the moment of torsion that the ring gear of sun gear applies to double the moment of torsion that is applied to sun gear, and must apply along same direction.The moment of torsion that is applied to carriage member must be in the moment of torsion sum on the moment of torsion and the ring gear that equal on the value on the sun gear and opposite with it on direction.
[0062] than the simple planetary group, in the dual planetary gear group, group planetary pinion and outer group planetary pinion can be realized the role exchange of ring gear and planet carrier parts in utilizing.For example, if sun gear is maintained fixed, then the planet carrier parts will be along the direction identical with ring gear rotation, but group planetary pinion and the planetary planet carrier parts of outer group will move rather than slower moving quickly than ring gear in having.
[0063] in interior group of planetary pinion with engagement and the planetary dual planetary gear group of outer group, the speed that the speed of ring gear and sun gear and planet carrier parts pass through respectively after the planet carrier parts number of teeth weighting that the sun gear number of teeth that planetary pinion fills and planetary pinion fill is proportional.For example, the difference of being filled by planetary pinion between ring gear and the sun gear may with the number of teeth as much on the sun gear in the same gear train.Under the sort of situation, the speed of ring gear will be 2/3 carriage member speed and 1/3 speed sun gear sum.If sun gear or planet carrier parts rotate in opposite direction, then the arithmetic sign of this speed is negative in mathematical computations.
[0064] if sun gear is maintained fixed, the group planetary pinion will rotate along the direction identical with the rotary annular gear of this gear train with the planetary carriage member of outer group in then having.On the other hand, if sun gear is maintained fixed and carriage member is driven, the planetary pinion that then engages sun gear in the internal tooth wheels will roll or " walking " along sun gear, thereby rotate along the direction identical with the carriage member rotation.Small gears with the pinion internal tooth wheels in the external tooth wheels will rotate in opposite direction, thereby force the ring gear of engagement to rotate in opposite direction, but just with respect to the planetary pinion that engages in the mode of engagement with ring gear.Planetary pinion in the external tooth wheels carries along the direction of carriage member.Effect that small gear in the external tooth wheels rotates on himself axis and the planetary pinion in the external tooth wheels be owing to the bigger effect of the orbiting that the carriage member motion causes is combined, thus ring gear along the direction rotation identical with carriage member but not as carriage member so fast.
[0065] if the carriage member in this kind dual planetary gear group is maintained fixed and the sun gear rotation, then ring gear will be with less speed and along the direction rotation identical with sun gear.If the ring gear of simple planetary group is maintained fixed and the sun gear rotation, then the planetary carriage member of the single group of supporting will be with less speed and along the direction rotation identical with sun gear.Therefore, we can easily observe, the single group planetary pinion that uses in the simple planetary group, and the role exchange between carriage member and the ring gear is caused by interior group of planetary pinion and the outer group planetary pinion that use is engaged with each other.
[0066] regular event of electrically variable transmission is that mechanical output is delivered to output from input.Transmit the part of action, a generator in two motor/generator as this as electric power.Another motor/generator is as motor and use this electric power.Along with the speed of exporting is increased at a high speed from zero, these two motor/ generators 80,82 little by little exchange the role as generator and motor, and can so exchange repeatedly.These exchanges occur in around the mechanical. points, and all are mechanically to transmit and do not have power to transmit in the mode of electricity basically from the power that is input to output basically in these mechanical. points.
[0067] at hybrid type electric variable formula speed variator system, battery 86 also can be supplied electric power to speed changer, or speed changer can be supplied power to battery.If a large amount of electric power of battery supplied are to speed changer (for example, be used for vehicle and quicken), then two motor/generators all can be used as motor.If speed changer supply electric power is to battery (for example, being used for energy storing brake), then two motor/generators all can be used as generator.During very near the mechanical. points of operation, because the electric loss in the system, two motor/generators also all can be used as generator and electric power output is less.
[0068] regular event with speed changer is opposite, and in fact speed changer can be used for mechanical output is passed to input from output.This can be used to replenish the energy storing brake of vehicle braked device and enhancing or additional vehicle in vehicle, especially when the descending slope of long distance.If make the power that flows through speed changer reverse in this way, then the role of motor/generator will be opposite with the role in the regular event.
Concrete operation Consideration
[0069] each embodiment disclosed herein has 17 kinds of functional requirements (its 17 row with each operator scheme table shown in the drawings are corresponding) that can be grouped into five kinds of operator schemes.These five kinds of operator schemes will be set forth hereinafter and can follow the table of operator scheme separately (for example, the operator scheme table of Fig. 1 b, 2b, 3b etc.) of each speed changer graphical diagram to understand better by reference.
[0070] first operator scheme is " a battery reverse gear mode ", and its first row (battery reverse gear) with each operator scheme table is corresponding, for example, and first row of the operator scheme table of Fig. 1 b.In this pattern, tail-off, and the transmission element that is connected to motor is not subjected to the control of Engine torque, however the residual torque that may exist some to cause because of engine revolution inertia.EVT is driven by the energy of a use in the motor/generator from battery, thereby causes the vehicle backward.According to kinetic energy configuration, in this pattern, another motor/generator is rotatable or can not rotate, but and transmitting torque or transmitting torque not.If another motor/generator rotation, then it is used for producing the energy that is stored in the battery.In the embodiment of Fig. 1 b, in the battery reverse gear mode, clutch 50 and break 55 are in jointing state, the moment of torsion of generator 80 be zero and motor 82 have-1.00 moment of torsion, and for example realized-2.88 torque ratio.In each operator scheme table, near (M) the torque value in motor/generator row 80 and 82 represents that this motor/generator as motor, does not have (M) to represent that then this motor/generator is as generator.
[0071] second operator scheme is " EVT reverse gear mode " (or mechanical reverse gear mode), and its second row (EVT reverse gear) with each operator scheme table is corresponding, for example second of the operator scheme table of Fig. 1 b row.In this pattern, EVT is by engine-driving and by a driving in the motor/generator.Another motor/generator is delivered to drive motor with the generator mode operation and with 100% produce power with returning.Final effect is the powered vehicle backward.With reference to Fig. 1 b, for example, in the EVT reverse gear mode, clutch 50 and break 55 are in jointing state, and generator 80 has the moment of torsion of-0.35 unit, and motor 82 has the moment of torsion of-3.55 units, and realizes-8.33 output torques corresponding to the Engine torque of 1 unit.
[0072] the 3rd operator scheme comprises " reverse gear and forward gears originate mode " (it is also referred to as " torque converter reverse gear and forward gears pattern "), its the third line and fourth line (torque converter reverse gear and torque converter forward gears) with each operator scheme table is corresponding, for example, the third line and the fourth line of the operator scheme table of Fig. 1 b.In this pattern, EVT is by engine-driving and by a driving in the motor/generator.The optional part of the energy that is produced in the generator unit is stored in the battery, and dump energy is delivered to motor.In Fig. 1, this part is about 99%.The speed changer output speed is about with the ratio (gear ratio) of engine speed+/-0.001 (positive sign represents that vehicle creeps forward, and negative sign is represented vehicle and creeped backward).With reference to Fig. 1 b, in the torque converter reverse gear mode, clutch 50 and break 55 are in jointing state, and motor/generator 80 is as the generator with-0.35 unit moment of torsion, motor/generator 82 is as the motor with-3.09 unit moments of torsion, and the torque ratio of realization-7.00.In torque converter forward gears pattern, clutch 50 and break 55 are in jointing state, motor/generator 80 is as the generator with-0.35 unit moment of torsion, and motor/generator 82 conducts have the motor of 0.98 unit moment of torsion, and realize 4.69 torque ratio.
[0073] the 4th operator scheme is " but continually varying slewing range pattern ", it comprises scope 1.1 operating points, scope 1.2 operating points, scope 1.3 operating points, scope 1.4 operating points, scope 2.1 operating points, scope 2.2 operating points, scope 2.3 operating points and scope 2.4 operating points, its 5-the 12nd row with each operating point table is corresponding, for example 5-the 12nd row of the operating point table of Fig. 1 b.In this pattern, EVT is driven by a motor/generator of operating as motor in motor and the motor/generator.Another motor/generator is operated as generator and 100% energy that produces is delivered to motor with returning.By the operating point of representatives such as scope 1.1,1.2... be the continuous forward velocity that provides of EVT than in discrete point.For example, in Fig. 1 b, be under the situation of jointing state, realized from 4.69 to 1.86 torque ratio scope at clutch 50 and break 55.Be at clutch 50 and 52 under the situation of jointing state, realized from 1.36 to 0.54 torque ratio scope.
[0074] the 5th operator scheme comprises " fixed ratio " pattern (R1, F1, F2, F3 and F4), and (that is, the operator scheme table) 13-17 is capable corresponding, and for example, the 13-17 of the operator scheme table of Fig. 1 b is capable for itself and each operator scheme table.In this operator scheme, transmission-like is similar to the ground operation of conventional automatic transmission, and wherein three torque transmitters are in jointing state to form discrete ratio.Follow each illustrated clutch table only to show four forward gears fixed ratio speed and a reverse gear fixed ratio speed, but can obtain extra fixed ratio.With reference to Fig. 1 b, in fixed ratio R1 (being the reverse gear fixed ratio), clutch 54 and break 55,57 are in the even twisting moment ratio of jointing state with realization-5.32.In fixed ratio F1, clutch 50,54 and break 55 are in jointing state to realize 2.86 even twisting moment ratio.In fixed ratio F2, clutch 50,52 and break 55 are in jointing state to realize 1.86 fixed ratio.In fixed ratio F3, clutch 50,52 and 54 is in jointing state to realize 1.00 fixed ratio.In fixed ratio F4, clutch 50,52 and break 58 are in jointing state to realize 0.53 fixed ratio.Therefore, each " X " in the motor/generator row 82 of Fig. 1 b represents that break 58 is in jointing state, and motor/generator 82 does not rotate.
[0075] dynamical system 10 can be operated with " electric quantity consumption pattern ".For the present invention, " electric quantity consumption pattern " is a kind ofly mainly to provide power by motor/generator for vehicle, makes the pattern that when vehicle arrives its destination battery 86 is depleted or almost exhaust.In other words, during the electric quantity consumption pattern, motor 12 only must guarantee that battery 86 does not have to operate under the depleted degree before arriving the destination.Traditional motor vehicle driven by mixed power is with " electric weight maintenance pattern " operation, if wherein battery charge level drops to predeterminated level (for example 25%) when following, motor automatically moves, with to battery charge.Therefore, by with electric quantity consumption pattern operation, motor vehicle driven by mixed power can be saved some or all fuel that will be used to keep 25% battery charge level in the conventional hybrid power car.Should be appreciated that then the dynamical system of motor vehicle driven by mixed power is preferably only operated with the electric quantity consumption pattern if battery 86 can recharge by being inserted in the energy source (not shown) after arriving the destination.
[0076] in addition, also can use various fuel to provide power, with the fuel saving of the efficient of improving concrete application as motor 12.These fuel can comprise (for example) gasoline, diesel oil, ethanol, dimethyl ether etc.
[0077] speed changer 14 can be operated with so-called monotype or double-mode (scope).In monotype, the torque transmitter that is in jointing state forward velocity than (by discrete point: scope 1.1,1.2,1.3 with 1.4 expressions) whole continuum in maintenance identical.In double-mode, the torque transmitter that is in jointing state switches in (for example, the scope among Fig. 1 2.1) under the velocity ratio of a certain centre.The speed changer of Fig. 4 a comprises the triplex mode performance.In triplex mode, the torque transmitter (for example, scope 3.1 among Fig. 4 b) under other intermediate speed ratio that is in jointing state switches.Depend on machine layout, the change of torque transmitter jointing state has the advantage that can reduce element speeds in the speed changer.
[0078] as mentioned above, the jointing state table of torque transmitter is shown in the operator scheme table and fixed ratio pattern list of Fig. 1 b.Fig. 1 b also provides the example of the torque ratio that can utilize the ring gear/sun gear gear ratio acquisition that provides with way of example among Fig. 1 b.N R1/ N S1Value is the gear ratio of planetary gear set 20; N R2/ N S2Value is the gear ratio of planetary gear set 30.In addition, icon among Fig. 1 b has also been described the ratio rank (ratio step) that utilize the gear ratio example of being given to be obtained.For example, fixedly the rank between the reverse gear torque ratio and the first fixed forward torque ratio are-1.86 than (step ratio), rank ratio between the first fixed forward torque ratio and the second fixed forward torque ratio is 1.54, rank ratio between the second fixed forward torque ratio and the 3rd fixed forward torque ratio is 1.86, rank ratio between the 3rd fixed forward torque ratio and the 4th fixed forward torque ratio is 1.86, and ratio ranges is 5.40.
The explanation of second exemplary embodiment
[0079] with reference to Fig. 2 a, shown dynamical system 110, it comprises another embodiment's who is connected to modified model electrically variable transmission (it is totally by numeral 114 expressions) motor 12.Speed changer 114 is designed for receiving at least a portion from the driving power of motor 12.
[0080] in this illustrated embodiment, motor 12 can be the mineral fuel motor equally, for example, easily is suitable for providing its diesel engine that available power of transmitting with constant per minute rotating speed (RPM) is usually exported.As shown in the figure, motor 12 has the output shaft as the input block 17 of speed changer 14.Transient torque damper (not shown) also may be implemented between the input block 17 of motor 12 and speed changer.
[0081] no matter which kind of means motor 12 adopts be connected to speed changer input block 17, and speed changer input block 17 all may be operably coupled to the planetary gear set in the speed changer 14.The output block 19 of speed changer 114 is connected to main reducing gear 16.
[0082] speed changer 114 utilizes two differential gear set of the character that preferably has planetary gear set 120 and 130.Planetary gear set 120 is used the outer gear part 124 that is commonly referred to ring gear.Ring gear component 124 is external in the internal gear part 122 that is commonly referred to sun gear.Carriage member 126 rotatably supports a plurality of planetary pinions 127, so that each planetary pinion 127 engages the outer ring geared parts 124 and the interior sun gear parts 122 of first planetary gear set 120 in the mode of engagement.
[0083] planetary gear set 130 has the outer gear part 134 that also is commonly referred to ring gear equally, and outer gear part 134 is external in the internal gear part 132 that is commonly referred to sun gear equally.A plurality of planetary pinions 137 also rotatably are installed in the carriage member 136, so that each planetary gear member 137 engages the outer ring geared parts 134 and the interior sun gear parts 132 of planetary gear set 130 simultaneously in the mode of engagement.
[0084] speed changer input block 17 is connected with the carriage member 126 of planetary gear set 120.Speed changer output block 19 is connected with the carriage member 136 of planetary gear set 130.
[0085] speed changer 114 also comprises first motor/generator 180 and second motor/generator 182.The stator of first motor/generator 180 is fixed to gearbox case 160.The rotor of first motor/generator 180 is fixed to the sun gear parts 122 of planetary gear set 120.
The stator of [0086] second motor/generator 182 also is fixed to gearbox case 160.The rotor of second motor/generator 182 is fixed to the sun gear parts 132 of planetary gear set 130.
[0087] first torque transmitter (for example, clutch 150) makes the sun gear parts 122 of planetary gear set 120 optionally be connected with the ring gear component 134 of planetary gear set 130.Second torque transmitter (for example, clutch 152) makes the ring gear component 124 of planetary gear set 120 optionally be connected with the sun gear parts 132 of planetary gear set 130.The 3rd torque transmitter (for example, clutch 154) makes the sun gear parts 122 of planetary gear set 120 optionally be connected with the sun gear parts 132 of planetary gear set 130.The 4th torque transmitter (for example, break 155) makes the ring gear component 134 of planetary gear set 130 optionally be connected with gearbox case 160.The 5th torque transmitter (for example, break 157) makes the ring gear component 124 of planetary gear set 120 optionally be connected with gearbox case 160.First torque transmitter 150, second torque transmitter 152, the 3rd torque transmitter 154, the 4th torque transmitter 155 and the 5th torque transmitter 157 are used to help to select the operator scheme of hybrid type speed changer 114.
[0088] turn back to elaboration about power source now, according to above stated specification and with reference to Fig. 2 a, be apparent that, speed changer 114 is from motor 12 received power optionally.The hybrid type speed changer also exchanges power with the electric power source 186 that may be operably coupled to controller 188.Electric power source 186 can be one or more batteries.Can use can provide or store and other electric power source (for example, fuel cell) of the electric power of providing and delivering substitutes battery, and can't change principle of the present invention.
[0089] as mentioned before, each embodiment has 17 kinds of functional requirements (its 17 row with each operator scheme table shown in the drawings are corresponding) that can be grouped into five kinds of operator schemes.First operator scheme is " a battery reverse gear mode ", and its first row (battery reverse gear) with the operator scheme table of Fig. 2 b is corresponding.In this pattern, tail-off, and in fact the transmission element that is connected to motor becomes the flywheel that is subjected to the engine inertia torque influence.EVT is driven by the energy of a use in the motor/generator from battery, thereby causes the vehicle backward.In this pattern, another motor/generator is rotatable or can not rotate.Shown in Fig. 2 b, in this pattern, break 155 is in jointing state, and motor/generator 180 has zero moment of torsion, and motor 182 has the moment of torsion of-1.00 units, and has for example realized-2.88 output torque.
[0090] second operator scheme is " EVT reverse gear mode " (or mechanical reverse gear mode), and its second row (EVT reverse gear) with the operator scheme table of Fig. 2 b is corresponding.In this pattern, EVT is by engine-driving and by a driving in the motor/generator.Another motor/generator is delivered to drive motor with the generator mode operation and with 100% produce power with returning.Final effect is the powered vehicle backward.In this pattern, clutch 152 and break 155 are in jointing state, and generator 180 has the moment of torsion of-0.35 unit, and motor 182 has the moment of torsion of-3.55 units, and have realized-8.33 output torques corresponding to the input torque of 1 unit.
[0091] the 3rd operator scheme comprises " reverse gear and forward gears originate mode ", its the third line and fourth line (torque converter reverse gear and torque converter forward gears) with each operator scheme table is corresponding, for example, the third line and the fourth line of the operator scheme table of Fig. 2 b.In this pattern, EVT is by engine-driving and by a driving in the motor/generator.The optional part of the energy that is produced in the generator unit is stored in the battery, and dump energy is delivered to motor.In the torque converter reverse gear, clutch 152 and break 155 are in jointing state, and motor/generator 180 is as the generator with-0.35 unit moment of torsion, and motor/generator 182 is as the motor with-3.09 unit moments of torsion, and the torque ratio of realization-7.00.In the torque converter forward gears, clutch 152 and break 155 are in jointing state, motor/generator 180 is as the generator with-0.35 unit moment of torsion, and motor/generator 182 conducts have the motor of 0.98 unit moment of torsion, and realize 4.69 torque ratio.For these torque ratios, about 99% of generator energy is stored in the battery.
[0092] the 4th operator scheme comprises scope 1.1 patterns, scope 1.2 patterns, scope 1.3 patterns, scope 1.4 patterns, scope 2.1 patterns, scope 2.2 patterns, scope 2.3 patterns and scope 2.4 patterns, and its 5-the 12nd row with the operator scheme table of Fig. 2 b is corresponding.In this pattern, EVT is driven by a motor/generator of operating as motor in motor and the motor/generator.Another motor/generator is operated as generator and 100% produce power is delivered to motor with returning.By the operating point of representatives such as scope 1.1,1.2... be the continuous forward velocity that provides of EVT than in discrete point.For example, in Fig. 2 b, be under the situation of jointing state, realized from 4.69 to 1.86 ratio ranges, and be at clutch 150 and 152 under the situation of jointing state, realized from 1.36 to 0.54 ratio ranges at clutch 152 and break 155.
[0093] the 5th operator scheme comprises " fixed ratio " pattern (F1, F2, F3, F4 and F5), its with Fig. 2 b in the 13-17 of operator scheme table capable corresponding.In this operator scheme, transmission-like is similar to the ground operation of conventional automatic transmission, and one of them torque transmitter is in jointing state to form discrete velocity ratio.In fixed ratio F1, clutch 152,154 and break 155 are in jointing state to realize 2.82 even twisting moment ratio.In fixed ratio F2, clutch 150,152 and break 155 are in jointing state to realize 1.74 fixed ratio.In fixed ratio F3, clutch 150,152 and 154 is in jointing state to realize 1.00 fixed ratio.In fixed ratio F4, clutch 150,152 and break 157 are in jointing state to realize 0.60 fixed ratio.In fixed ratio F5, clutch 150,154 and break 157 are in jointing state to realize 0.39 fixed ratio.
[0094] as mentioned above, the jointing state table of torque transmitter is shown in the operator scheme table and fixed ratio pattern list of Fig. 2 b.Fig. 2 b also provides the example of the torque ratio that can utilize the ring gear/sun gear gear ratio acquisition that provides with way of example among Fig. 2 b.N R1/ N S1Value is the gear ratio of planetary gear set 120, N R2/ N S2Value is the gear ratio of planetary gear set 130.In addition, the chart of Fig. 2 b has been described the ratio rank that utilize the gear ratio example of being given to be obtained.For example, the rank ratio between first fixed forward grade of torque ratio and the second fixed forward grade of torque ratio is 1.63, and ratio ranges is 7.32.
The explanation of the 3rd exemplary embodiment
[0095] with reference to Fig. 3 a, shown dynamical system 210, it comprises another embodiment's who is connected to modified model electrically variable transmission (it is totally by numeral 214 expressions) motor 12.Speed changer 214 is designed for receiving its at least a portion from the driving power of motor 12.As shown in the figure, motor 12 has the output shaft as the input block 17 of speed changer 214.Transient torque damper (not shown) also may be implemented between the input block 17 of motor 12 and speed changer 214.
[0096] no matter which kind of means motor 12 adopts be connected to speed changer input block 17, and the speed changer input block all may be operably coupled to the planetary gear set in the speed changer 214.The output block 19 of speed changer 214 is connected to main reducing gear 16.
[0097] speed changer 214 utilizes two differential gear set of the character that preferably has planetary gear set 220 and 230.Planetary gear set 220 is used the outer gear part 224 that is commonly referred to ring gear.Ring gear component 224 is external in the internal gear part 222 that is commonly referred to sun gear.Carriage member 226 rotatably supports a plurality of planetary pinions 227,228, so as each planetary pinion 227 engage in the mode of engagement in sun gear parts 222 and each planetary pinion 228 engage the outer ring geared parts 224 and the corresponding planetary pinion 227 of first planetary gear set 220 simultaneously in the mode of engagement.
[0098] planetary gear set 230 has the outer ring geared parts 234 that is external in interior sun gear parts 232 equally.A plurality of planetary pinions 237 also rotatably are installed in the carriage member 236, so that each planetary gear member 237 engages the outer ring geared parts 234 and the interior sun gear parts 232 of planetary gear set 230 simultaneously in the mode of engagement.
[0099] speed changer output block 19 is connected to carriage member 236.
[00100] speed changer 214 also comprises first motor/generator 280 and second motor/generator 282 respectively.The stator of first motor/generator 280 is fixed to gearbox case 260.The rotor of first motor/generator 280 is fixed to sun gear parts 222.The stator of second motor/generator 282 also is fixed to gearbox case 260.The rotor of second motor/generator 280 is fixed to sun gear parts 232.
[00101] first torque transmitter (for example, input clutch 150) makes ring gear component 224 optionally be connected with input block 17.Second torque transmitter (for example, clutch 252) makes sun gear parts 222 optionally be connected with ring gear component 234.The 3rd torque transmitter (for example, input clutch 254) makes sun gear parts 222 optionally be connected with input block 17.The 4th torque transmitter (for example, break 255) makes ring gear component 234 optionally be connected with gearbox case 260.The 5th torque transmitter (for example, break 257) makes ring gear component 224 optionally be connected with gearbox case 260.The 6th torque transmitter (for example, break 258) and 282 parallel connections of motor/generator optionally to brake its rotation.First torque transmitter 250, second torque transmitter 252, the 3rd torque transmitter 254, the 4th torque transmitter 255, the 5th torque transmitter 257 and the 6th torque transmitter 258 are used to help to select the operator scheme of hybrid type speed changer 214.
[00102] hybrid type speed changer 214 is from motor 12 received powers, and electric power source 286 received powers from may be operably coupled to controller 288.
[00103] operator scheme of Fig. 3 b has been expressed clutch, motor/generator state and the output/input ratio of six kinds of operator schemes of speed changer 214.These patterns comprise: foregoing " battery reverse gear mode " (battery reverse gear), " EVT reverse gear mode " (EVT reverse gear), " reverse gear and forward gears originate mode " (torque converter reverse gear and torque converter forward gears), " scope 1.1,1.2,1.3... pattern " and " fixed ratio pattern " (R1, F1, F2, F3 and F4).
[00104] as mentioned above, the jointing state table of torque transmitter is shown in the operator scheme table and fixed ratio pattern list of Fig. 3 b.Fig. 3 b also provides the example of the torque ratio that can utilize the ring gear/sun gear gear ratio acquisition that provides with way of example among Fig. 3 b.N R1/ N S1Value is the gear ratio of planetary gear set 220; N R2/ N S2Value is the gear ratio of planetary gear set 230.In addition, the chart of Fig. 3 b has been described the ratio rank that utilize the gear ratio example of being given to be obtained.For example, the rank ratio between first fixed forward grade of torque ratio and the second fixed forward grade of torque ratio is 1.54, and ratio ranges is 5.40.
The explanation of the 4th exemplary embodiment
[00105] with reference to Fig. 4 a, shown dynamical system 310, it comprises another embodiment's who is connected to modified model electrically variable transmission (it is totally by numeral 314 expressions) motor 12.Speed changer 314 is designed for receiving at least a portion from the driving power of motor 12.
[00106] as shown in the figure, motor 12 has the output shaft as the input block 17 of speed changer 314.Transient torque damper (not shown) also may be implemented between the input block 17 of motor 12 and speed changer.
[00107] no matter which kind of means motor 12 adopts be connected to speed changer input block 17, and speed changer input block 17 all may be operably coupled to the planetary gear set in the speed changer 314.The output block 19 of speed changer 314 is connected to main reducing gear 16.
[00108] speed changer 314 utilizes two planetary gear set 320 and 330.The outer ring geared parts 324 of sun gear parts 322 in planetary gear set 320 is used and is external in.Carriage member 326 rotatably supports a plurality of planetary pinions 327, so that each planetary pinion 327 engages the outer ring geared parts 324 and the interior sun gear parts 322 of first planetary gear set 320 in the mode of engagement.
[00109] planetary gear set 330 also has the outer ring geared parts 334 that is external in interior sun gear parts 332.Carriage member 336 rotatably supports a plurality of planetary pinions 337,338, so that each planetary pinion 337 engages outer ring geared parts 324 and each planetary pinion 338 engages planetary gear set 330 simultaneously in the mode of engagement interior sun gear parts 332 and corresponding planetary pinion 337 in the mode of engagement.
[00110] speed changer output block 19 is connected with ring gear component 334.
[00111] speed changer 314 also comprises first motor/generator 380 and second motor/generator 382 respectively.The stator of first motor/generator 380 is fixed to gearbox case 360.The rotor of first motor/generator 380 can optionally be connected with sun gear parts 322 with ring gear component 334 via dog-clutch 392, thereby replaces between position A and B respectively.The rotor of first motor/generator 380 is connected to dog-clutch 392 via inclined to one side gearing.As skilled in the art to understand, within the scope of the invention, a pair of torque transmitter can be used for realizing the selective engagement that obtained by dog-clutch 392.
The stator of [00112] second motor/generator 382 also is fixed to gearbox case 360.The rotor of second motor/generator 382 is fixed to sun gear parts 332.
[00113] first torque transmitter (for example, input clutch 350) makes carriage member 326 optionally be connected with input block.Second torque transmitter (for example, clutch 352) makes sun gear parts 322 optionally be connected with carriage member 336.The 3rd torque transmitter (for example, input clutch 354) makes sun gear parts 322 optionally be connected with input block 17.The 4th torque transmitter (for example, break 355) makes carriage member 336 optionally be connected with gearbox case 360.The 5th torque transmitter (for example, break 357) makes carriage member 326 optionally be connected with gearbox case 360.The 6th torque transmitter (for example, break 358) and 382 parallel connections of motor/generator optionally to brake its rotation.First torque transmitter 350, second torque transmitter 352, the 3rd torque transmitter 354 and the 4th torque transmitter 355, the 5th torque transmitter 357, the 6th torque transmitter 358 and dog-clutch 392 are used to help the operator scheme of selective transmission 314.
[00114] hybrid type speed changer 314 is from motor 12 received powers, and with the electric power source 386 exchange power that may be operably coupled to controller 388.
[00115] operator scheme of Fig. 4 b has been expressed clutch, motor/generator state and the output/input ratio of five kinds of operator schemes of speed changer 314.These patterns comprise: foregoing " battery reverse gear mode " (battery reverse gear), " EVT reverse gear mode " (EVT reverse gear), " reverse gear and forward gears originate mode " (torque converter reverse gear and torque converter forward gears) but continually varying slewing range pattern (" scope 1.1,1.2,1.3... ") and " fixed ratio pattern " (R1, F1, F2, F3 and F4).
[00116] as mentioned above, the jointing state table of torque transmitter is shown in the operator scheme table and fixed ratio pattern list of Fig. 4 b.Fig. 4 b also provides the example of the torque ratio that can utilize the ring gear/sun gear gear ratio acquisition that provides with way of example among Fig. 4 b.N R1/ N S1Value is the gear ratio of planetary gear set 320; N R2/ N S2Value is the gear ratio of planetary gear set 330.In addition, the chart of Fig. 4 b has been described the ratio rank that utilize the gear ratio example of being given to be obtained.For example, the rank ratio between first fixed forward grade of torque ratio and the second fixed forward grade of torque ratio is 1.54, and ratio ranges is 5.40.
[00117] in claims, language " by connecting constantly " or " connecting constantly " are meant direct connection or suitably gear connection, for example, and with respect to the gearing of off-axis line.In addition, " fixed component " or " " can comprise gearbox case (housing) or (a plurality of) any other non-rotating member.In addition, when mentioning torque-transmitting mechanisms something is connected to the parts of gear train, it also can be connected to the interconnecting member that it is connected with these parts.Should be further understood that, can be combined in the scope of claims from the different characteristic of different embodiments of the invention.
[00118], it should be understood that those skilled in the art of the present technique are easy to the principle of the invention is made a lot of changes although disclose a plurality of preferred embodiment of the present invention.Therefore, the scope of the invention is not to be defined in details shown and that describe, but intention is included in all changes and modification in claims scope.

Claims (17)

1. electrically variable transmission, it comprises:
Be used for from the input block of motor received power;
Output block;
First motor/generator and second motor/generator;
First differential gear set and second differential gear set, it respectively has first parts, second parts and the 3rd parts;
Described input block is connected constantly or optionally with at least one parts of described gear train, and described output block is connected constantly with another parts of described gear train;
Described first motor/generator is connected constantly with the parts of described first planetary gear set or optionally is connected via the parts of dog-clutch with described first gear train or second gear train;
Described second motor/generator is connected constantly with the parts of described first gear train or second gear train;
First torque transmitter, it makes the parts of described first gear train optionally be connected with the parts of described input block or described second gear train;
Second torque transmitter, it makes the parts of described second gear train optionally be connected with the parts of described first gear train;
The 3rd torque transmitter, it makes the parts of described first gear train optionally be connected with the parts or the described input block of described second gear train;
The 4th torque transmitter, it makes the parts of described first gear train optionally be connected with fixed component;
The 5th torque transmitter, it makes the parts of described second gear train optionally be connected with described fixed component; And
Wherein, described first torque transmitter, second torque transmitter, the 3rd torque transmitter, the 4th torque transmitter and the 5th torque transmitter can engage, but have the electrically variable transmission of continually varying speed than scope and at least four fixed forward velocity ratios to provide.
2. electrically variable transmission as claimed in claim 1 is characterized in that, described first differential gear set and second differential gear set are planetary gear set.
3. electrically variable transmission as claimed in claim 2 is characterized in that, the carriage member of each in the described planetary gear set is single small gear carriage member.
4. electrically variable transmission as claimed in claim 2 is characterized in that, at least one carriage member of described planetary gear set is the double pinion carriage member.
5. electrically variable transmission as claimed in claim 1, it is characterized in that, described first torque transmitter, second torque transmitter, the 3rd torque transmitter, the 4th torque transmitter, the 5th torque transmitter and described first motor/generator and second motor/generator can be operated, so that five kinds of operator schemes to be provided in described electrically variable transmission, but it comprises battery reverse gear mode, EVT reverse gear mode, reverse gear and forward gears originate mode continually varying slewing range pattern and fixed ratio pattern.
6. electrically variable transmission as claimed in claim 1 is characterized in that, described electrically variable transmission also comprises:
Interconnecting member, it makes described first parts of described first gear train be connected constantly with described first parts of described second gear train.
7. electrically variable transmission as claimed in claim 6 is characterized in that, described electrically variable transmission also comprises:
The 6th torque transmitter, it is connected with a motor/generator in second motor/generator is parallel with described first motor/generator, optionally to prevent described motor/generator rotation; And
Wherein, described first torque transmitter, second torque transmitter, the 3rd torque transmitter, the 4th torque transmitter, the 5th torque transmitter, the 6th torque transmitter and described first motor/generator and second motor/generator can be operated, so that five kinds of operator schemes to be provided in described electrically variable transmission, but it comprises battery reverse gear mode, EVT reverse gear mode, reverse gear and forward gears originate mode continually varying slewing range pattern and fixed ratio pattern, comprising the mechanical reverse ratio.
8. electrically variable transmission, it comprises:
Be used for from the input block of motor received power;
Output block;
First motor/generator and second motor/generator;
First differential gear set and second differential gear set, it respectively has first parts, second parts and the 3rd parts;
Described input block is connected constantly or optionally with at least one parts of described gear train, and described output block is connected constantly with another parts of described gear train;
Described first motor/generator is connected constantly with the parts of described first gear train or optionally is connected via the parts of dog-clutch with described first gear train or second gear train;
Described second motor/generator is connected constantly with the parts of described first gear train or second gear train;
First torque transmitter, second torque transmitter, the 3rd torque transmitter, the 4th torque transmitter and the 5th torque transmitter, it is used to make the described parts and the described input block of described first gear train and second gear train, the miscellaneous part of fixed component or described planetary gear set optionally connects, described first torque transmitter, second torque transmitter, the 3rd torque transmitter, the 4th torque transmitter and the 5th torque transmitter can engage, but have the electrically variable transmission of continually varying speed than scope and at least four fixed forward velocity ratios between described input block and the described output block to be provided at.
9. electrically variable transmission as claimed in claim 8, it is characterized in that, described first differential gear set and second differential gear set are planetary gear set, and described first torque transmitter makes the parts of described first planetary gear set optionally be connected with the parts of described input block or described second gear train.
10. electrically variable transmission as claimed in claim 9 is characterized in that, described second torque transmitter makes the parts of described second planetary gear set optionally be connected with the parts of described first gear train.
11. electrically variable transmission as claimed in claim 10 is characterized in that, described the 3rd torque transmitter makes the parts of described first gear train optionally be connected with the parts or the described input block of described second gear train.
12. electrically variable transmission as claimed in claim 11 is characterized in that, described the 4th torque transmitter makes the parts of described first gear train optionally be connected with described fixed component.
13. electrically variable transmission as claimed in claim 12 is characterized in that, described the 5th torque transmitter makes the parts of described second gear train optionally be connected with described fixed component.
14. electrically variable transmission as claimed in claim 13 is characterized in that, described electrically variable transmission also comprises:
Interconnecting member, it makes described first parts of described first gear train be connected with described first parts of described second gear train.
15. electrically variable transmission as claimed in claim 14 is characterized in that, described electrically variable transmission also comprises:
The 6th torque transmitter, it is connected with a motor/generator in the described motor/generator is parallel, optionally to prevent described motor/generator rotation.
16. electrically variable transmission as claimed in claim 8 is characterized in that, the carriage member of each in the described planetary gear set is single small gear carriage member.
17. electrically variable transmission as claimed in claim 8 is characterized in that, at least one carriage member of described planetary gear set is the double pinion carriage member.
CN2007800192141A 2006-05-25 2007-05-17 Two-planetary electrically variable transmissions with multiple fixed ratios Active CN101454595B (en)

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US11/440,762 US7473199B2 (en) 2006-05-25 2006-05-25 Two-planetary electrically variable transmissions with multiple fixed ratios
PCT/US2007/069089 WO2007140123A2 (en) 2006-05-25 2007-05-17 Two-planetary electrically variable transmissions with multiple fixed ratios

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Cited By (5)

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